Pumping apparatus



Feb. 13, 1940. 1 s, FULLER 2,189,893

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ATTORNEYS ,5 ,of the well is actuated through a line oi fsucker Thus, in the UDSIOKG, the Counterhalanoe Weight v`Patenierll Febi13,19i y t t, t t

2,189,893 PUMPmo APPARATUS .i'ohn Fuller,` ,Tulsa, Okla., assigner to Oil Well Supply Company, Dallas, Tex., a corpora- 4tion'olf New `ersey Application July 15, 1937, Serial No. 153,823

` a claims. (ci. "zi- 48)r My invention relatesto apparatus for pumping that the `greatest mechanical advantage is ex-V deep Wells,` as for example `Welis for the producerted by the counterbalance Weight during the tion of` petroleum. In: the pumpingV of sueh upstroke and correspondingly `diminished me- Wells, the piston of a pump loeated at the bottom ohanicai advantage exerted on the downstroke.

l t UNITED!" STATES ff PATENT 'orties l rods connected end to endv and reaching to `a may act on the Walking he'amor equivalent ele` pumping mechanism atthe top of the Weil.` The merli? O the pumping appara-WS `With a 'ealel" top end of the line of sucker rods is' connected `moment arm than on the downstroke. For exthrough `any suitable means, usually through aY ample, a Counterbalancedl `crank arm having (if, y,polish rod extending through a pao at the Weight/swaty a iixed radius from the axial center ,in stop" of the Well tubing to a walking beam or of the crankarm may act through a crank arm pumpingjaok, which gives the'iine of sucker rods 0H a GVEI" 01r Walking beam at a gleatel dtae and the'pump piston an -upand down oscillation.` vfIOm the aXal Center of the latter during the j I1; is apparent that the" entire Weigh@ ofthe upstrokethan during the downstroke and in this sucker rods and of the pump piston, diminished Way give an eiective longer moment arm to the :1.5 by the buoyant eiiect of the liquid they displace,` 3' COllIltelbaanCe Weights during the ,UPSITOKS' and is at al1 times suspended `from vthe end vof the a diminished moment arm durilflg` the d0Wnwalking beam,`pumping jack, or other apparatus, `Str0ke Whichwould cause an added burden to the walks, I also PIOVQ `an apparatus Wheelih@ fOlCQ 201mg beam in its upward stroke'and an accelerato from the engines can likewise have an effective 52,0'` ing force in its downward stroke. leverage Change aS Wel- Y Q i The weight of the Sucker rods and pump pis- The Various features of they invention are illuston have heretofore beencounterbalancedby a ,trated by Way 0f example in the aCCOmpalYUg Weight mounted on acrank arm of the pu-rnping` drawings, in Whichl f V v apparatus, If the moment arm or torqueofthis .'Fg- 1 iS a Side elevatrland Eig-22a plan 0f va 25 yicounterbalance be made yjust equal to the ydis-- pumping apparatus embodyng'a Pfeffer-Ted Ol'Yll .placement VWeight of pump piston and sucker f the invention; Fis. 31S a chart showing the rods lsuspended from the Walking beam, the torqueS 0n the Walking beam'orctank the Coun v torque m the pumping apparatus during Sundownterbalancing torque ofthe .counterbalance Weight strokelbeing balanced in both directions, `Winoo and the resultant gear torque inthe apparatus y30.

yzero. On the upstroke, the ,torque Willbe that embOdyIlg my inVSntmmFig. i is4 a similar dia* imlosed by 'the weight of` liquid being lifted and i gram Showing a typical torque in apparatus hat the power required to give it the necessaryl'up ing a counterhalance Weight of constant mechanward acceleration. VThe net Weight of sucker Cal adVantage 01.7 moment ttm? Figs# 5 6 and ,7 f

- :is rods and pump piston is, of. course, baianeuin are, respectively, front elevations and sections a5 uns upper` stroke. intrus case, the torqueV win Gn the lines iff-4 and 5 5 0f a modid form 0f vary from Zero on the 1down stroketo a maXil Crank afm applcabte'to the apparat@ showt@ m mum on the upstroke, this maximum being, Figs? l and 2? Figs 3: 9 and 10 are respectively t therefore, about `twiceV the average 'or mean longitudinal Sectionsand .a Cross'sectot 0f ,the

4() torque If the net Weightfof the sucker rods t Crankrm ptn? Figs' 11, 12. 13 and 1431*@ espe' ,-40

and pump piston be overbalanced, the maximum tively *Side eleVatiOn, plan end elevation and SEC-M torque `required on the upstroke will `be corretion 0in une t4-*M 0f Fig 11 Ofplmpng 3D' t` `spondingiy reduced, but there will be an accelerparams' embdyng another form 0f the nven* v ating torque on the downk stroke, Heretofore, tion; Fig. 15 is a View similar to that of Fig. il t therefore, it has been impossible to avoid a'vvide 0n a SmaHeT-Scale Showing Ce'ti'tm tf'tfts ofthe ,45

Avariation in the torque required to pump .the Well. apparatus disconnected; 15 S a Veta end My invention, gyeatly minimizes and largdy View of a part of the apparatus taken `fromthe yeliminates these" variations in pumping torque left OfFig- 15- i t required .to pump a well and provides means `loy Referring more pariiulallyi@ the pumping 1o which wells may be pumped` with a torque that apparatus kSllDWIl in Figs- 1` t0 19 inclusive, the

varies only slightly from the mean throughout a end, or end connection, of a line of sucker rods f complete pumpingcycle. l l 20 indicated `by the dot and dash line of Fig`-` 1 Y I In my invention. I provide a counterhaiance is connected by means of a link il to iambealn f Weight thatvacts on the pumping apparatus with hanger 22 mounted on one end of a Walking l a lvarying mechanical advantage in such a. Way beam 23- The other end 0f the Walking beam 2,3, g5

`180 degrees from that of Fig. l. 'ance to rotation is shown as positive and acis journalled in a pair of bearings M supported on an upright pedestal or postv 25 commonly known as a Samson post. This post may be braced by a bracing strut 2t and is mounted on.

the base frame 27 of the pumping apparatus. The walking beam 23 is rocked or oscillated vertically on its supporting pivot in the bearings 2li by power supplied from a prime mover, such as the internal combustion or other engine 28.

`Power is transmitted from the engine 28 through against the plate 34 alternately lifts and .lowers the beam 23.

It will be apparent that the moment arm of `the 'suspended sucker rods and pump elements thanv during the upstroke because the crank arm isthen on the opposite side of its center of rotation, bringing the axial center of the roller 23 nearer the center of the bearings 2li. Accordingly, the change in the moment arm of this crank varies the torque exerted by the counter- Weight between the upstroke and downstroke to more nearly approximate the changed load on the sucker rod line.

This is shown graphically in Fig. 3 of the drawings, in which the ordinates express in inch pounds the resistance to rotation exerted by the counterbalance and the walking beam, respectively, for eachA angle starting with the position As the resistcelerating torques as negative, the resultant force to be driven by the gears or the gear torque required to drive the crank shaft.

torque requiredy to drive the crank shaft will the crank arm 32 will be in its lovverrnostv posiv tion. As it swings upwardly, the crank torque rises rapidly to about 100,000 inch pounds at the 180 degree mark, While the counterbalance torque has dropped correspondingly to a negative value crank torque would be larger than 100,000 inch pounds, except for the fact that the effective moment arm of the crank roller 33, has now been increased from that of its starting position by an amount equal to twice the radius of the crank arm. In passing to the 270 degree angle and thence `to the original position, the crank torque decreases and the counterbalance torque increases until they ,reach the -`same magnitudes as at their starting position.

It is to be noted that the resulting gear torque obtained by the algebraic sum of the crank torque and counterbalance torque does not become negative and varies only slightly from the mean' Atorque indicated in broken lines as 17,000 inch4 pounds. Thus'the actual gear torque in this particular example does not drop to 10,000 inch pounds, nor rise above 24,000 inch pounds l and is generally well within these limits at all angles. Moreover, it is to bernoticed that there are no sharp or steep changes in the resulting gear torque.

In Fig. 4, the torques are plotted in a similar Amanner for corresponding installation, in which the crank arm Wasconnected to the Walking beam, by a pitman as in installations prior to my inventio-'rrv In this case, it was necessary `to usea somewhat larger counterbalance torque, namely, 87,000 inch pounds maximum instead of 81,700 inch pounds maximum as in Fig. 3. This is because the crank torque is subjected to wider variations, varying from 60,000 inch pounds to' .about 115,000 inch pounds. As shown in Fig. 4,

the .gear torque obtained by the algebraic addition of the crank torque and counterbalance torque varies widely and sharply from the mean torque. At its maximum, it is very nearlytwice the mean torque'ancl at its minimum, it is actually negative, so that the resultant of the crank torque and counterbalance torque actually tend order to drive the apparatus during the upstroke and require'heavier counterbalance Weights and heavierstructure throughout in order to stand the maximum stresses and the sudden changes orv shocks imposed. In contrast, thechanging mechanical advantage obtained in applicants invention enables a much smaller power unit to be `employed with smaller and lighter construction and With less wear due to reversals and sudden variations in thev driving stressesy or power.

Moreover, the period of upstroke is increased and L that of the doWnstroke decreased, the upstroke starting before and lasting until after 270 from the starting point of the graph, Whereas in the graph of Fig. 4the upstroke starting exactly at 90 and terminating at 270from the starting position.v l

Where the pumping power is to be used under such conditions that the stroke of the pump is to be varied or changed, the crank arm .32 must be lengthened or shortened accordingly. In the modification shown in Figs. 5, 6 and 7, amcdied form of crank arm is provided, in which 'three crank arm lengths may be obtained selectively.

In thismodication, a hub 35 is mounted `on a crank shaft 3l and carries a crank arm ring 36 having three crank lpin openings 31, 38 and 39 of progressively larger radius from the axis of-the` shaft 3l. The crank ring 36 is bolted to a a'nge di] of the hub by means of bolts r4| and is keyed theretoby keys 42 inserted in common keyways between' the-hub and crankl ring. twillfbe apparent, therefore, thatfthe crank iingisreplace- 4 `'able and when mounted in position is rigidly series on its free end aroller t5, as shownin Figs.

`8, 9`an` l i0. rhe pin i3 `may be removably se- `cured and rotates with the crank shaft V3l.' A

crank pin d'3 may be inserted:selectivelylnany` fexample by the roller-bearingelements d5 acting between' an 4outer raceway i? in the roller Mi and` an inner raceway'formedby the pints; lThe roller elements are `enclosedfat one `end 'by means l'of a gasket type oiclosure-it and the othery by f'a'plate 4S, -'so as to form a closed chamber, in

f which a lubricant `may be carried to besupplied to the `roller `elements throughthe canal system 50; e willjbe -ap'parent that by changing the pin 43 -irom one to vthe other of the three openings 3l, SSvand 35i, threedifferent crank arm'radii y-inay be vobtained selectively. vAlsothat thecrank nliub may be replacedl by other crank hubs having different crank armfradii, or by a singlecrank armffThe `action in any` oasev is smilarto that illustrated in connection withFigs. land 2 and` Chart 3. i

'I'lfieabove'descrbed apparatus of Figs. 1 to 10, inclusive, is particularly advantageous because it provides the longest possible lever arm for a beam of a given length, thereby reducing the angle and the side sway on the sucker rod line for a iven lift. Special hangers to compensate for this side sway may generally be avoided by the form of the invention shown in Figs.- I to 10. However, the invention may also be applied to pumping power in which the beam is suspended midway of its ends, and may thus be applied to existing pumping apparatus. A modification of this type is shownin Figs. 11 to l6`inclusive. In

ythis modification thewalking beam 5I Iis. pivotally supported onthe Samson post 52 by means of a beam saddle or bearing 53 Which-may be provided with the usual headache post 54 to support the pumping end of the beam, or to be disconnected for changesor repairs. The pumping end of the beamis provided with ra hanger 5,5 above the center line of the well or in alignment with, the sucker vrod asindicated in the dot and dash lines.' 'Ihe opposite end ofthe beam is connected by means of a pitman 5E to or pump operatingmeans. e v e The pump driving mechanism is driven from a the driving pulley 5l through a speed reduction mechanism 58 which drives a rotating shaft 59 onj'the'end of which isa crank arm 5U. On the end of the crank arm is mounted a Wrist pin El which,

in turn, carries a rotatable wheel or roller B2. Ihe wheel 52 rides freely on a lever beam 63 pivoted at one end on a bearing or fulcrum 64 on the Samson post 52, and connected at its other end t0 the pitman v through a connecting bearing 65. The roller 52 is preferably provided with flanges t6, as shown in Fig. i4,y to ensure its accurate travel on the beam E3. The lever beam 53 is-held upwardly against the roller t2 by the weight vof the'pumping apparatus acting through the Walking beam 5l and the pitman 55. The roller 62 and the lever beam @3 may be additionally held in association by the guide 6l mounted.v on the lever beam 63 and extending over the pulley B2. A counter-weight 68 isalso mounted on the shaft 59 either asian integralpart of the crankr, or `iiwl'ependently thereof', butin rigid relation theretoso thatthe weight of thecounter-Weight acts through the crank 6B on the lever beamls.`

In the operation of the apparatus, the 4shaft i 59 andi-.he crank Stand counter-weight es rotate counter-clockwise as indicated by the arrow in Fig. 11.,` During the downstroke of the` crank,

` it tilts fthe-lever beam (i3 downwardly about its fulcrumk 64 andcarries with it thel pitman 55 n10 andthe'left 'arm of the walking beam 5|, thereby tilting upwardly theY opposite arm. and carrying with itthe sucker rod line of the pump. As the crankv swings from its lowermost position counterclockwisetoits uppermost position, the beam 51h16r4 moves upwardly and permits the'walking beaml to swing clockwise to lower the opposite end to which the pumping mechanism is attached` through the hanger 55. t

`During the' downstroke, the the leverbeam 63 with a greater moment arm 'than during the upstroke inasmuch as the Adistance of the fulcrum 55 from the wheel 62,

.through which `the power andweight "of the counter-weight 53 are transmitted through thei126 lever beam 53, 1is greater on the downstrokethan'V on theupstroke. Accordinglypthe effect `of the' counter-weight is increased during the upstroke ofthe suckeri'rod line, anddecreased `during the downstroke; thereby compensating V'for 'the 11n-4&0`

equal lpull ofgthe line during the respectivestrokes. The result is similar to that shown in Fig. 3.

In the construction shown iny Figs. 11 to`16, it is `at times desirable to use the walking beam 5i for drilling, or cleaning outoperations. `In .35 this case the variable` counter-weight B8 is not required. `The lever beam 53 is disconnected and the walking beam 5I is driven directly from `the crank E15. For this apparatus Ythe connection of the pitman 55 to the walking beam 5| is shifted 40 by moving a connecting hanger 59 from the position shown in Fig. 11 to that shown in Fig. 15. The roller or wheel 62 is disconnected from the crankarm, and connecting the bearing 66 vof the pitman directly tothe end of the crank arm 60. 45

In the operation ofthe apparatus, unequal stresses may at times be imposed on the shaft 59 which, being transmitted to the gearing, would cause unequal wear on the latter. To compensate for this wear, the crank arm 50 is keyed to 50 theshaft`59 lby a plurality of keys 10, three being shown byway of example, so that the position i of the crank 6l) relatively to the transmission gearsfmay be adjusted to equalize the wear. 'In order'to hold the walking beam stationary While 55 adjusting the pump mechanism, a brake drum 'Il is providedon `the driving shaft of the speed mechanism 58 on which a brake band 'I2 may be caused to operate by a lever 13 and control rod 14.

By means of the above invention it is; therefore, possible to so counter-balance the driving apparatus as tov maintain a torque resistance against Vthe driving gear that is very nearly constant and approximately that of the mean stroke. As a result of this and of the lessening or elimination of shock `due to sudden changes in, or reversals of, the torque resistance against the driving gears, a smaller power equipment is re-` quired and the entire construction may be made 70 i of the downstroke period are` also of advantage,

affording more time` to get the liquid into motion f `during the'upstroke for a given speed of driving. 7o

crank 6G acts onrylll` The modicati'on 'shown in Figs. l to l0 inclusive, has the furtheradvantages of a longer angle arm and less deviation of the free end of the walking beam from vertical alignment with the well "e5 and also, inasmuch as the greatest weight is supported nearer tothe pull of the pump and'sucker line, this beam or lever may be made of somewhat lighter construction.

The modication shown in Fig. il has the fur 1,210 ther advantage of eliminating any horizontal thrust on the Samson post as all of the forces acting on the walking beam are in a vertical plane.

What I claim is: l. Well pumping apparatus comprising combination a walking beam, means to pivotally sustain said beam for vertical oscillation, a pump mechanism dependingly secured from the beam at a fixed distance from the pivotal point of the "'20 beam, and means including a rotating crank arm to apply power to the beam intermediate the pivotal point and the point oi suspension of said pump mechanism, said means including means to progressively shift the point of application of 5125 power away from and towards the said pivotal n point to obtain a maximum moment arm at the time ofA maximum load during the upstroke of the pump mechanism-and a minimum moment arm at the time of minimum load during the downv30 stroke of the pump mechanism, and a counterbalance weight secured to rotatevabout the axis of rotation of the crankv shafty supporting said crank arm in a position relative to the crank arm vto effectively balance the load of said pump mechand the ,point of suspension of said pump mechanism comprises a crank pin mounted on said crank arm and a roller mounted on said crank pin and means locating the crank arm, pin and roller in a position to operatively engage the roller with the said walking beam thereby to raise and lower the said beam during rotative movement of the said crank arm and pin. p l

A3. The combination of claim l, wherein said means to apply power to the said beam comprises a crank shaft rotatively driven, a crank arm mounted on said shaft, a roller pin extension on said 'crank arm and means to position the crank shaft, crank arm and roller pin extension in a position between the pivotal point and the point of suspension onthe beam with the axis oi the roller pinextension normal to the beam axis and with the roller surface in engagement with the under side of the said beam in all positions of rotation of the said crank arm, and a bearing plate member on the under side of the beam covering the beam surface contacting said roller.

JOHN s. FULLER. 

